US12259187B2 - Heat exchange system, and fin structure of heat exchanger - Google Patents

Heat exchange system, and fin structure of heat exchanger Download PDF

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Publication number
US12259187B2
US12259187B2 US17/912,120 US202117912120A US12259187B2 US 12259187 B2 US12259187 B2 US 12259187B2 US 202117912120 A US202117912120 A US 202117912120A US 12259187 B2 US12259187 B2 US 12259187B2
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heat exchange
flow path
mode
fin portions
heat exchanger
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US20230160637A1 (en
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Shota HANAFUSA
Kenji Ando
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Sumitomo Precision Products Co Ltd
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Sumitomo Precision Products Co Ltd
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Assigned to SUMITOMO PRECISION PRODUCTS CO., LTD. reassignment SUMITOMO PRECISION PRODUCTS CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ANDO, KENJI, HANAFUSA, Shota
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0233—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels
    • F28D1/024—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with air flow channels with an air driving element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans

Definitions

  • the present invention relates to a heat exchange system and a fin structure of a heat exchanger, and in particular, to a heat exchange system and a fin structure of a heat exchanger that perform heat exchange by natural convection and heat exchange by forcing air to flow in.
  • a heat exchange system and a fin structure of a heat exchanger that perform heat exchange by natural convection and heat exchange by forcing air to flow in are known.
  • Such a heat exchange system is disclosed in, for example, JP-S61-197416U.
  • JP-S61-197416U discloses a heat exchanger including a plurality of conduits, a connecting pipe having a U shape that connects the conduits, a plurality of fins, and a motor fan.
  • the plurality of conduits are disposed in parallel and have end portions connected by the connecting pipe having a U shape.
  • the plurality of fins are disposed to form a forced convection part with a narrowed pitch (disposition interval) and natural convection parts.
  • the forced convection part is provided in a central portion of the plurality of fins, and the natural convection parts are provided on right and left sides of the forced convection part.
  • the motor fan is provided in the forced convection part.
  • the heat exchanger disclosed in JP-S61-197416U is configured to switch between natural convection and forced convection as needed to perform cooling (heat exchange).
  • the forced convection part disclosed in JP-S61-197416U since the forced convection part disclosed in JP-S61-197416U has the disposition interval of the fins narrower (smaller) than in the natural convection parts, the forced convection part increases in flow path resistance. In such a configuration, though not clearly stated in JP-S61-197416U, the forced convection part cannot be used in heat exchange by natural convection. For this reason, in the configuration disclosed in JP-S61-197416U, heat exchange by natural convection is performed only in the natural convection parts, and heat exchange by forcing air to flow in is performed only in the forced convection part.
  • the plurality of fins are divided into fins used only in heat exchange by natural convection and fins used only in heat exchange by forcing air to flow in. That is, since a part of the plurality of fins is used only in heat exchange by natural convection, and the remaining fins are used only in heat exchange by forcing air to flow in, the number of fins used in heat exchange by natural convection and the number of fins used in heat exchange by forcing air to flow in decrease compared to a configuration in which heat exchange is performed using all fins. For this reason, in a case of switching between performing heat exchange by natural convection and heat exchange by forcing air to flow in, there is a problem in that heat exchange efficiency of respective heat exchange is degraded.
  • the invention has been accomplished to solve the problem described above, and an object of the invention is to provide a heat exchange system and a fin structure of a heat exchanger capable of, in a case of switching between performing heat exchange by natural convection and heat exchange by forcing air to flow in, suppressing degradation of heat exchange efficiency of respective heat exchange.
  • the present inventors have conducted intensive studies and have found that a plurality of fin portions in a first flow path of a heat exchanger undulate to be usable in both heat exchange by natural convection and heat exchange by forcing air to flow into the first flow path.
  • a heat exchange system includes a heat exchanger including a base portion that comes into contact with a heat exchange target, and a first flow path which is divided by a plurality of fin portions extending upward from the base portion and through which air flows, a fan that makes air flow into the first flow path, and a control unit that performs control for switching between a first mode where heat exchange of the heat exchange target is performed by forcing air to flow into the first flow path with the fan and a second mode where the heat exchange of the heat exchange target is performed by natural convection, in which the plurality of fin portions are disposed in parallel at predetermined intervals in a width direction of the first flow path, the plurality of fin portions are formed to have an undulating shape from one end toward the other end of the first flow path in the width direction of the first flow path, and the first flow path is configured to be used in both the first mode and the second mode.
  • the plurality of fin portions are disposed in parallel at the predetermined intervals in the width direction of the first flow path through which air flows, and are formed to have the undulating shape from one end toward the other end of the first flow path in the width direction of the first flow path, and the first flow path is configured to be used in both the first mode where the heat exchange is performed by forcing air to flow in and the second mode where the heat exchange is performed by the natural convection.
  • the first flow path is used in both the first mode and the second mode, it is possible to suppress a decrease in the number of fin portions used in each heat exchange mode, compared to a configuration in which fin portions including both fin portions used only in the first mode and fin portions used only in the second mode are provided in the first flow path.
  • the plurality of fin portions have the undulating shape in the width direction of the first flow path, it is possible to promote heat transfer with turbulence of flown-in air, compared to a configuration in which the plurality of fin portions do not have an undulating shape. It is possible to increase a heat transfer area without narrowing the disposition interval of the fin portions. As a result, in a case of switching between performing heat exchange by natural convection and heat exchange by forcing air to flow in, it is possible to suppress degradation of heat exchange efficiency of respective heat exchange.
  • the plurality of fin portions are provided continuously from the one end to the other end of the first flow path and undulate periodically such that the other end of the first flow path is visible as viewed from the one end of the first flow path.
  • a through flow path is formed in the first flow path. Accordingly, it is possible to suppress an increase in pressure loss of air flowing in the first flow path, compared to a configuration in which a through flow path is not formed in the first flow path with the plurality of fin portions.
  • the plurality of fin portions have the undulating shape, it is possible to secure heat exchange efficiency in the second mode where heat exchange is performed by natural convection.
  • the plurality of fin portions are provided continuously from the one end to the other end of the first flow path and undulate periodically such that the other end of the first flow path is visible as viewed from the one end of the first flow path, preferably, the plurality of fin portions undulate such that an undulating pattern of the same waveform is repeated at a fixed undulation width in the width direction of the first flow path, and the undulation width is at least a size less than a half of a disposition interval of the plurality of fin portions.
  • the plurality of fin portions undulate such that the undulating pattern of the same waveform is repeated at the fixed undulation width in the width direction of the first flow path, it is possible to simplify the structure (shape) of the plurality of fin portions, compared to a configuration in which the undulation width and/or the undulating pattern of the plurality of fin portions is different halfway. Since the undulation width of the plurality of fin portions is at least the size less than a half of the disposition interval of the plurality of fin portions, it is possible to make a configuration in which the other end of the first flow path is visible as viewed from the one end of the first flow path, and to secure heat exchange efficiency in the second mode. As a result, it is possible to achieve both the simplification of the structure (shape) of the plurality of fin portions and securing of heat exchange efficiency in the second mode.
  • the plurality of fin portions undulate such that an undulating pattern of the same waveform is repeated at a fixed undulation width in the width direction of the first flow path, the undulating pattern includes a crest portion that protrudes to one side, a trough portion that protrudes to the other side, and a connecting portion that connects the crest portion and the trough portion, in the width direction of the first flow path, and a maximum inclination angle of the connecting portion with respect to a direction from one end side to the other end side of the first flow path is within an angle range of equal to or greater than 10 degrees and equal to or less than 30 degrees.
  • a disposition interval of the plurality of fin portions is within a range of equal to or greater than 5 mm and equal to or less than 10 mm.
  • the plurality of fin portions are disposed at equal intervals over a whole width in the width direction of the first flow path.
  • the control unit is configured to switch between the first mode and the second mode based on a temperature of the heat exchange target.
  • the heat exchange target includes a heat exchange target fluid
  • the heat exchanger further includes a second flow path through which the heat exchange target fluid flows in a state of being in contact with the base portion where a plurality of fin portions are provided.
  • a fin structure of a heat exchanger includes a base portion that comes into contact with a heat exchange target, and a plurality of fin portions provided to extend upward from the base portion, in which the plurality of fin portions form a first flow path through which air flows, have an undulating shape from one end toward the other end of the formed first flow path in a width direction of the first flow path, are disposed at equal intervals over a whole width in the width direction of the first flow path, are provided continuously from the one end to the other end of the first flow path, and, undulate periodically such that the other end of the first flow path is visible as viewed from the one end of the first flow path, and in performing heat exchange of the heat exchange target, the first flow path is configured to be used in both forced heat exchange where the heat exchange of the heat exchange target is performed by forcing air to flow into the first flow path and natural heat exchange where the heat exchange of the heat exchange target is performed by natural convection.
  • the plurality of fin portions are disposed in parallel at the predetermined intervals in the width direction of the first flow path, and have the undulating shape from one end toward the other end of the first flow path in the width direction of the first flow path.
  • the plurality of fin portions are disposed at the equal intervals over the whole width in the width direction of the first flow path, it is possible to perform heat exchange by the first mode and heat exchange by the second mode using the whole first flow path, unlike a configuration in which a part where heat exchange is performed by the first mode and a part where heat exchange is performed by the second mode are formed by changing the disposition interval of the plurality of fin portions halfway of the first flow path. As a result, it is possible to suppress degradation of heat exchange efficiency of each heat exchange mode.
  • the plurality of fin portions are provided continuously from one end to the other end of the first flow path, and undulate periodically such that the other end of the first flow path is visible as viewed from one end of the first flow path.
  • a through flow path is formed in the first flow path. Accordingly, it is possible to suppress an increase in pressure loss of air flowing in the first flow path, compared to a configuration in which a through flow path is not formed in the first flow path with the plurality of fin portions.
  • the plurality of fin portions have the undulating shape, it is possible to secure heat exchange efficiency in the second mode where heat exchange is performed by natural convection.
  • FIG. 1 is a perspective view showing a heat exchange system according to a first embodiment.
  • FIG. 2 is a perspective view showing a base portion and a plurality of fin portions of a heat exchanger according to the first embodiment.
  • FIG. 3 is a schematic view as a first flow path according to the first embodiment is viewed from an X1 direction.
  • FIG. 4 is a schematic view as the first flow path according to the first embodiment is viewed from a Z1 direction.
  • FIG. 5 is a simulation result showing change in heat exchange amount in changing a front face wind velocity using the heat exchanger according to the first embodiment and a heat exchanger according to a comparative example.
  • FIG. 6 is a simulation result showing change in pressure loss in changing the front face wind velocity using the heat exchanger according to the first embodiment and the heat exchanger according to the comparative example.
  • FIG. 7 is a flowchart illustrating processing in which the heat exchange system according to the first embodiment switches between a first mode and a second mode.
  • FIG. 8 is a schematic view illustrating a maximum inclination angle of a connecting portion according to a second embodiment.
  • FIG. 9 is a schematic view (A) to a schematic view (F) illustrating a heat exchanger used in a simulation according to the second embodiment and a heat exchanger of a comparative example.
  • FIG. 10 is a simulation result showing change in heat exchange amount in changing a front face wind velocity in the heat exchanger according to the second embodiment in which an angle of a connecting portion of a first flow path and a period are made different.
  • FIG. 11 is a simulation result showing change in pressure loss in changing the front face wind velocity in the heat exchanger according to the second embodiment in which the angle of the connecting portion of the first flow path and the period are made different.
  • FIG. 12 is a perspective view showing a base portion and a plurality of fin portions of a heat exchanger according to a modification example.
  • a heat exchange system 100 includes a heat exchanger 1 , a fan 2 , a control unit 3 , a first temperature sensor 4 , and a second temperature sensor 5 .
  • an up-down direction is represented as a Z direction
  • an up direction is represented as a Z1 direction
  • a down direction is represented as a Z2 direction.
  • Two directions perpendicular to each other within a plane perpendicular to the Z direction are represented as an X direction and a Y direction.
  • the X direction one side is represented as an X1 direction
  • the other side is represented as an X2 direction.
  • the Y direction one side is represented as a Y1 direction
  • the other side is represented as a Y2 direction.
  • the heat exchanger 1 has an opening that is an inlet or an outlet of a fluid and is configured to make the fluid flow to perform heat exchange.
  • FIG. 1 shows an example where the heat exchanger 1 is a plate fin type heat exchanger.
  • the plate fin type heat exchanger 1 has a rectangular parallelepiped shape including a surface (side surface) where the opening is formed.
  • the heat exchanger 1 has a flow path for making the fluid flow inside and is configured to perform heat exchange in a process of making the fluid flow.
  • the heat exchange that is performed by the heat exchanger 1 includes cooling and heating. In the present embodiment, a case where the heat exchanger 1 performs cooling of a heat exchange target will be described.
  • the heat exchanger 1 has a structure in which separate plates 10 , first corrugated fins 13 , and second corrugated fins 14 are laminated.
  • First side bars 15 are disposed on in outer peripheral portions of each first corrugated fin 13 .
  • Second side bars 16 are disposed in outer peripheral portions of each second corrugated fin 14 .
  • the first corrugated fins 13 , the second corrugated fins 14 , the separate plates 10 , the first side bars 15 , and the second side bars 16 are bonded by brazing, whereby the heat exchanger 1 is configured.
  • Each separate plate 10 is an example of a “base portion” in the claims.
  • a first flow path 11 is divided by the separate plate 10 , the first side bar 15 , and the separate plate 10 , and is configured with each layer where the first corrugated fin 13 is disposed inside. Air as the fluid flows in the first flow path 11 .
  • the first flow path 11 is formed to extend in the up-down direction (Z direction).
  • the Y direction is a width direction of the first flow path 11 .
  • the X direction is a height direction of the first flow path 11 .
  • a second flow path 12 is divided by the separate plate 10 , the second side bar 16 , and the separate plate 10 , and is configured with each layer where the second corrugated fin 14 is disposed inside.
  • a heat exchange target fluid flows in the second flow path 12 in a state of being in contact with the separate plate 10 .
  • the heat exchanger 1 performs heat exchange between air and the heat exchange target fluid flowing in the first flow path 11 and the second flow path 12 , respectively.
  • air flows into the first flow path 11 from a Z2 direction side and flows out from a Z1 direction side.
  • the heat exchange target fluid flows into the second flow path 12 from a Y1 direction side and flows out from a Y2 direction side.
  • the separate plate 10 has a rectangular shape.
  • the separate plate 10 is configured to come into contact with the heat exchange target.
  • the heat exchange target includes the heat exchange target fluid.
  • the heat exchange target fluid includes, for example, oil or a refrigerant.
  • the heat exchanger 1 has a structure in which the first flow path 11 and the second flow path 12 are alternately laminated such that the first flow path 11 and the second flow path 12 are perpendicular to each other.
  • the first flow path 11 and the second flow path 12 are laminated in the X direction.
  • the heat exchanger 1 includes surfaces 1 a where an opening 11 a of the first flow path 11 is formed and surfaces 1 b where an opening 12 a of the second flow path 12 is formed.
  • the opening 11 a of the first flow path 11 is formed in both surfaces 1 a in the Z direction and the opening 12 a of the second flow path 12 is formed in both surfaces 1 b on a Y direction side perpendicular to the surface 1 a .
  • the opening 11 a is formed in a portion of the surface 1 a excluding the second flow path 12 .
  • the opening 12 a is formed in a portion of the surface 1 b excluding the first flow path 11 .
  • the fan 2 is configured to make air flow into the first flow path 11 under the control of the control unit 3 .
  • the fan 2 is configured to make air flow into the first flow path 11 from the opening 11 a on the Z2 direction side.
  • the fan 2 is provided in a state of being in contact with the surface 1 a on the Z2 direction side to close the opening 11 a on the Z2 direction side.
  • the fan 2 includes, for example, a blower that blows air into the first flow path 11 .
  • the control unit 3 is configured to perform control for switching between a first mode where the heat exchange of the heat exchange target is performed by forcing air to flow into the first flow path 11 with the fan 2 and a second mode where the heat exchange of the heat exchange target is performed by natural convection.
  • the control unit 3 is configured to acquire a temperature difference between air and the heat exchange target based on a temperature of air acquired by the first temperature sensor 4 and a temperature of the heat exchange target acquired by the second temperature sensor 5 .
  • the first flow path 11 is configured to be used in both the first mode and the second mode.
  • the control unit 3 includes, for example, a central processing unit (CPU), a read only memory (ROM), and a random access memory (RAM).
  • the first temperature sensor 4 is configured to acquire the temperature of air.
  • the first temperature sensor 4 is provided in the vicinity of the opening 11 a on the Z2 direction side and acquires the temperature of air flowing into the first flow path 11 .
  • the first temperature sensor 4 is configured to output the acquired temperature of air to the control unit 3 .
  • the first flow path 11 is formed by the separate plate 10 and one first corrugated fin 13 .
  • the separate plate 10 on an X1 direction side is not shown.
  • the separate plate 10 extends along a YZ plane.
  • the separate plate 10 has long sides disposed in an orientation along the Z direction.
  • the first corrugated fin 13 includes a plurality of fin portions 13 a , a first connecting portion 13 b , and a second connecting portion 13 c .
  • the plurality of fin portions 13 a are provided to extend upward from the separate plate 10 .
  • the plurality of fin portions 13 a are provided to extend upward from the separate plate 10 from an X2 direction side toward the X1 direction side.
  • the plurality of fin portions 13 a are connected by the first connecting portion 13 b on the X1 direction side.
  • the plurality of fin portions 13 a are connected by the second connecting portion 13 c on the X2 direction side.
  • the first connecting portion 13 b and the second connecting portion 13 c are alternately provided in the Y direction.
  • the first flow path 11 is divided by the plurality of fin portions 13 a provided to extend upward from the separate plate 10 .
  • the plurality of fin portions 13 a are disposed in parallel at predetermined intervals p 1 in the width direction (Y direction) of the first flow path 11 .
  • the plurality of fin portions 13 a are formed to have an undulating shape from one end 11 b toward the other end 11 c of the first flow path 11 in the width direction (Y direction) of the first flow path 11 .
  • the plurality of fin portions 13 a are disposed at the intervals p 1 and at equal intervals over the whole width in the width direction (Y direction) of the first flow path 11 .
  • the interval p 1 of the plurality of fin portions 13 a is a distance of a gap portion of the fin portions 13 a excluding a plate thickness.
  • the undulating shape is a shape in which a crest portion 11 d and a trough portion 11 e are alternately repeated in a direction (Z direction) from one end 11 b toward the other end 11 c of the first flow path 11 .
  • the plurality of fin portions 13 a undulate in a period p 2 .
  • the period p 2 is a distance between the crest portions 11 d on the Y1 direction side of the fin portion 13 a in the Z direction.
  • the plurality of fin portions 13 a undulate such that an undulating pattern of the same waveform is repeated at a fixed undulation width W in the width direction (Y direction) of the first flow path 11 .
  • the undulation width W is a distance between the crest portion 11 d on the Y1 direction side of the fin portion 13 a and the trough portion 11 e on the Y1 direction side of the fin portion 13 a .
  • the undulating pattern means a unit of repetition in the Z direction in a case where the plurality of fin portions 13 a undulate.
  • the distance between a trough portion 11 g on the Y2 direction side of the fin portion 13 a and a crest portion 11 f on the Y2 direction side of the fin portion 13 a is equal to the distance between the crest portion 11 d on the Y1 direction side of the fin portion 13 a and the trough portion 11 e on the Y1 direction side of the fin portion 13 a.
  • FIG. 4 is a schematic view as the first flow path 11 is viewed from the Z1 direction side.
  • FIG. 4 shows the fin portions 13 a , the first connecting portion 13 b , the second connecting portions 13 c , a surface 110 a in the crest portion 11 d (see FIG. 3 ) of the fin portion 13 a that is visible from the Z2 direction side, a surface 110 b in the trough portion 11 e (see FIG. 3 ) of the fin portion 13 a that is visible from the Z2 direction side, a surface 110 c in the crest portion 11 f (see FIG. 3 ) of the fin portion 13 a that is visible from the Z2 direction side, and a surface 110 d in the trough portion 11 g (see FIG.
  • FIG. 4 is not a sectional view, and the separate plate 10 , the fin portions 13 a , the first connecting portion 13 b , the second connecting portions 13 c , and the surface 110 a to the surface 110 d are hatched differently for ease of identification.
  • the plurality of fin portions 13 a undulate periodically such that the other end 11 c of the first flow path 11 is visible as viewed from one end 11 b of the first flow path 11 .
  • the undulation width W is at least a size less than a half of the interval p 1 of the plurality of fin portions 13 a .
  • the plurality of fin portions 13 a undulate such that a distance D between an end portion 111 a on the Y2 direction side of the surface 110 b and an end portion 111 b on the Y1 direction side of the surface 110 c is not 0 (zero).
  • the plurality of fin portions 13 a undulate such that a size obtained by adding a width W 1 in the Y direction of the surface 110 b and a width W 2 in the Y direction of the surface 110 c of each of the plurality of fin portions 13 a is smaller than the interval p 1 of the plurality of fin portions 13 a .
  • the interval p 1 of the plurality of fin portions 13 a is within a range of equal to or greater than 5 mm and equal to or less than 10 mm.
  • the interval p 1 of the plurality of fin portions 13 a is, for example, about 8 mm.
  • a thickness of the first fin portion is about 0.25 mm.
  • the first flow path 11 in performing the heat exchange of the heat exchange target, is used in both forced heat exchange where the heat exchange of the heat exchange target is performed by forcing air to flow into the first flow path 11 and natural heat exchange where the heat exchange of the heat exchange target is performed by natural convection.
  • the heat exchanger 1 according to the present embodiment can be used in both forced heat exchange and natural heat exchange by performing a simulation using the heat exchanger 1 according to the present embodiment and the comparative example.
  • a simulation result described below is obtained by cooling the heat exchange target using the heat exchanger 1 according to the embodiment and a comparative example.
  • a graph G 1 shown in FIG. 5 shows change in heat exchange amount in changing a front face wind velocity using the heat exchanger 1 in the present embodiment and a heat exchanger according to the comparative example.
  • the graph G 1 takes a heat exchange amount (kW: kilowatt) as the vertical axis and takes a front face wind velocity (m/s: millimeters per second) as the horizontal axis.
  • the front face wind velocity is a wind velocity of air in the opening 11 a in flowing into the heat exchanger 1 , and is not a wind velocity of air that flows among the plurality of fin portions 13 a .
  • the simulation result shown in the graph G 1 is a result obtained by performing a simulation in a state where a temperature of air in the opening 11 a in flowing into the first flow path 11 is fixed at 30 degrees, and a temperature of the heat exchange target fluid that flows in the second flow path 12 is fixed at 85 degrees.
  • a heat exchanger in which fins having a thickness of about 0.25 mm are disposed at disposition intervals of about 8 mm is used.
  • a heat exchanger for natural heat exchange that includes fins disposed suitably for natural heat exchange and a heat exchanger for forced heat exchange that includes fins suitable for forced heat exchange are used.
  • the heat exchanger for natural heat exchange is, for example, a heat exchanger in which fins having a thickness of about 0.25 mm are disposed at disposition intervals of about 8 mm.
  • the heat exchanger for forced heat exchange is, for example, a heat exchanger in which fins having a thickness of about 0.25 mm are disposed at disposition intervals of about 3.4 mm.
  • Both the fins of the heat exchanger for natural heat exchange and the fins of the heat exchanger for forced heat exchange do not have an undulating shape from one end toward the other end of the first flow path in the Y direction.
  • the fins of the heat exchanger for natural heat exchange and the fins of the heat exchanger for forced heat exchange are configured with plain type corrugated fins.
  • a simulation result of the heat exchanger 1 according to the present embodiment is shown by a solid line 20 .
  • a simulation result of the heat exchanger for natural heat exchange is shown by a broken line 21 .
  • a simulation result of the heat exchanger for forced heat exchange is shown by a one-dot chain line 22 .
  • a value of a simulation result by natural heat exchange is shown at a position where the front face wind velocity is 0 (zero).
  • a result shows that the heat exchange amount of the heat exchanger for natural heat exchange is the greatest, and the heat exchange amount of the heat exchanger 1 according to the present embodiment is the second greatest, and the heat exchange amount of the heat exchanger for forced heat exchange is the smallest.
  • a case where the front face wind velocity is 0 (zero) is heat exchange by natural convection. That is, a case where the front face wind velocity is 0 (zero) is heat exchange by the second mode.
  • a case where the front face wind velocity is equal to or higher than 0 (zero) is heat exchange by the first mode.
  • the heat exchange amount of the heat exchanger for forced heat exchange is the greatest, and the heat exchange amount of the heat exchanger for natural heat exchange is the smallest.
  • the heat exchange amount of the heat exchanger for forced heat exchange is the greatest, and the heat exchange amount of the heat exchanger for natural heat exchange is the smallest.
  • the heat exchange amount of the heat exchanger 1 according to the present embodiment is the greatest, and the heat exchange amount of the heat exchanger for natural heat exchange is the smallest.
  • a ratio of the heat exchange amount of the heat exchanger 1 according to the present embodiment to the heat exchange amount of the heat exchanger for forced heat exchange is about 96%.
  • a ratio of the heat exchange amount of the heat exchanger for natural heat exchange to the heat exchange amount of the heat exchanger for forced heat exchange is about 39%.
  • a ratio of the heat exchange amount of the heat exchanger 1 according to the present embodiment to the heat exchange amount of the heat exchanger for forced heat exchange is about 112%.
  • a ratio of the heat exchange amount of the heat exchanger for natural heat exchange to the heat exchange amount of the heat exchanger for forced heat exchange is about 40%. That is, it has been confirmed that the heat exchanger 1 according to the present embodiment has heat exchange efficiency equal to or higher than the heat exchanger for forced heat exchange in the heat exchange by the first mode.
  • a ratio of the heat exchange amount of the heat exchanger 1 according to the present embodiment to the heat exchange amount of the heat exchanger for natural heat exchange is about 93%.
  • a ratio of the heat exchange amount of the heat exchanger for forced heat exchange to the heat exchange amount of the heat exchanger for natural heat exchange is about 39%. That is, it has been confirmed that the heat exchanger 1 according to the present embodiment has heat exchange efficiency equal to the heat exchanger for natural heat exchange in the heat exchange by the second mode. With this, it has been confirmed that the heat exchanger 1 according to the present embodiment can be used in both the first mode and the second mode.
  • a graph G 2 shown in FIG. 6 shows change in pressure loss in changing the front face wind velocity using the heat exchanger 1 in the present embodiment and the heat exchanger according to the comparative example.
  • the graph G 2 takes a pressure loss (Pa: pascal) as the vertical axis and takes a front face wind velocity (m/s: millimeters per second) as the horizontal axis.
  • a simulation is performed using the heat exchanger 1 according to the present embodiment, the heat exchanger for natural heat exchange, and the heat exchanger for forced heat exchange.
  • a simulation result of the heat exchanger 1 according to the present embodiment is shown by a solid line 23 .
  • a simulation result of the heat exchanger for natural heat exchange is shown by a broken line 24 .
  • a simulation result of the heat exchanger for forced heat exchange is shown by a one-dot chain line 25 .
  • a value of the simulation result by natural heat exchange is shown at a position where the front face wind velocity is 0 (zero).
  • the pressure loss is 0 (zero).
  • a result shows that the pressure loss of the heat exchanger for forced heat exchange is the greatest, and the pressure loss of the heat exchanger for natural heat exchange is the smallest.
  • a result shows that the pressure loss of the heat exchanger 1 according to the present embodiment is the greatest, and the heat exchange amount of the heat exchanger for natural heat exchange is the smallest.
  • the heat exchanger 1 according to the present embodiment can be used in the heat exchange by the first mode.
  • the disposition interval of the fins is greater than the fins of the heat exchanger for forced heat exchange, it is considered that the pressure loss greater than the fins of the heat exchanger for forced heat exchange is generated in the vicinity of 1.5 (m/s) since forming of turbulence with an increase in wind velocity is promoted by the undulating shape of the first fin portion.
  • the heat exchanger 1 according to the present embodiment can be used in the heat exchange by the second mode. With this, it has been confirmed that the heat exchanger 1 according to the present embodiment can be used in both the first mode and the second mode.
  • control unit 3 is configured to switch between the first mode and the second mode based on the temperature of the heat exchange target. Specifically, the control unit 3 forces air to flow into the first flow path 11 with the fan 2 such that the temperature of the heat exchange target fluid flowing into the second flow path 12 acquired by the second temperature sensor 5 is equal to or lower than a predetermined temperature. In the present embodiment, the control unit 3 acquires a difference between the temperature of air flowing into the first flow path 11 acquired by the first temperature sensor 4 and the temperature of the heat exchange target fluid flowing into the second flow path 12 acquired by the second temperature sensor 5 .
  • the control unit 3 adjusts an inflow amount of air by the fan 2 based on the acquired temperature difference between air flowing into the first flow path 11 and the heat exchange target fluid flowing into the second flow path 12 . That is, in a case where the temperature difference between air and the heat exchange target is small, the control unit 3 increases the inflow amount of air by the fan 2 . In a case where the temperature difference between air and the heat exchange target is large, the control unit 3 decreases the inflow amount of air by the fan 2 .
  • the control unit 3 stops the operation of the fan 2 in a case where the acquired temperature difference between air flowing into the first flow path 11 and the heat exchange target fluid flowing into the second flow path 12 is large, and the needed heat exchange amount is decreased. That is, the control unit 3 performs control for performing heat exchange in the second mode. In performing heat exchange in the second mode, the fan 2 is stopped. Accordingly, air passes through the gap of the fan 2 by natural convection, and flows into the first flow path 11 from the opening 11 a on the Z2 direction side.
  • Step S 1 the control unit 3 determines whether or not an operation input to start automatic switching between natural heat exchange and forced heat exchange is performed. In a case where the operation input to start automatic switching is performed, the process proceeds to Step S 2 . In a case where the operation input to start automatic switching is not performed, the processing of Step S 1 is repeated.
  • Step S 2 the control unit 3 acquires the temperature of the heat exchange target fluid flowing into the second flow path 12 . Specifically, the control unit 3 acquires the temperature of the heat exchange target fluid flowing into the second flow path 12 with the second temperature sensor 5 (see FIG. 1 ).
  • Step S 3 the control unit 3 determines whether or not the temperature of the heat exchange target fluid is equal to or higher than the predetermined temperature. In a case where the temperature of the heat exchange target fluid is equal to or higher than the predetermined temperature, the process proceeds to Step S 4 . In a case where the temperature of the heat exchange target fluid is lower than the predetermined temperature, the process proceeds to Step S 5 .
  • Step S 4 the control unit 3 performs switching to the second mode. Specifically, the control unit 3 performs switching to the second mode by stopping the fan 2 . In a case where the fan 2 is stopped, the processing of Step S 4 is omitted. That is, in a case where the operation is performed in the second mode, the processing of Step S 4 is omitted.
  • Step S 5 the control unit 3 performs switching to the first mode. Specifically, the control unit 3 performs switching to the first mode by operating the fan 2 .
  • the control unit 3 may control the amount of air flowing into the first flow path 11 with the fan 2 based on the temperature of air acquired by the first temperature sensor 4 . In a case where the fan 2 is being operated, the processing of Step S 5 is omitted.
  • Step S 6 the control unit 3 determines whether or not an operation input to end automatic switching is performed. In a case where the operation input to end automatic switching is not performed, the process proceeds to Step S 2 . In a case where the operation input to end automatic switching is performed, the process ends.
  • the plurality of fin portions 13 a are disposed in parallel at the predetermined intervals p 1 in the width direction (Y direction) of the first flow path 11 through which air flows, and are formed to have the undulating shape from one end 11 b toward the other end 11 c of the first flow path 11 in the width direction of the first flow path 11 , the first flow path 11 is configured to be used in both the first mode where heat exchange is performed by forcing air to flow in and the second mode where heat exchange is performed by natural convection.
  • the first flow path 11 is used in both the first mode and the second mode, it is possible to restrain the structure of the heat exchanger 1 from being complicated, compared to a configuration in which both flow paths of a flow path for a first mode and a flow path for a second mode are provided.
  • the plurality of fin portions 13 a have the undulating shape in the width direction (Y direction) of the first flow path 11 , it is possible to promote heat transfer with turbulence of flown-in air, compared to a configuration in which the plurality of fin portions 13 a do not have the undulating shape. It is also possible to increase a heat transfer area. As a result, it is possible to switch between performing heat exchange by natural convection and heat exchange by forcing air to flow in, and to restrain the structure of the heat exchanger 1 from being complicated.
  • the plurality of fin portions 13 a are provided continuously from one end 11 b to the other end 11 c of the first flow path 11 , and undulate periodically such that the other end of the first flow path 11 is visible as viewed from one end 11 b of the first flow path 11 , a through flow path is formed in the first flow path 11 . Accordingly, it is possible to suppress an increase in pressure loss of air flowing in the first flow path 11 , compared to a configuration in which a through flow path is not formed in the first flow path 11 with the plurality of fin portions 13 a . As a result, even in a case where the plurality of fin portions 13 a have the undulating shape, it is possible to secure heat exchange efficiency in the second mode where heat exchange is performed by natural convection.
  • the plurality of fin portions 13 a undulate such that the undulating pattern having the same waveform is repeated at the fixed undulation width W in the width direction (Y direction) of the first flow path 11 , and the undulation width W is at least a size less than a half of the interval p 1 of the plurality of fin portions 13 a .
  • the plurality of fin portions 13 a undulate such that the undulating pattern having the same waveform is repeated at the fixed undulation width W in the width direction (Y direction) of the first flow path 11 .
  • the undulation width W of the plurality of fin portions 13 a is at least the size less than a half of the disposition interval p 1 of the plurality of fin portions 13 a .
  • the interval p 1 of the plurality of fin portions 13 a is within a range of equal to or greater than 5 mm and equal to or less than 10 mm, it is possible to dispose the plurality of fin portions 13 a at intervals suitable for the second mode where heat exchange is performed by natural convection.
  • the disposition interval of the plurality of fin portions 13 a is set within the range, while high performance is obtained in the second mode where heat exchange is performed by natural convection of air, the disposition interval is large for the first mode where heat exchange is performed by forcing air to flow in.
  • the plurality of fin portions 13 a are disposed at the equal intervals over the whole width in the width direction (Y direction) of the first flow path 11 .
  • it is possible to perform heat exchange by the first mode and heat exchange by the second mode using the whole first flow path 11 unlike a configuration in which a part where heat exchange is performed by the first mode and a part where heat exchange is performed by the second mode are formed by changing the interval p 1 of the plurality of fin portions 13 a halfway of the first flow path 11 .
  • control unit 3 Since the control unit 3 is configured to switch between the first mode and the second mode based on the temperature of the heat exchange target, the first mode and the second mode are switched based on the temperature of the heat exchange target. Accordingly, it is possible to suppress an increase in power consumption, for example, compared to a configuration in which heat exchange is constantly performed by the first mode. It is also possible to efficiently perform the heat exchange of the heat exchange target, for example, compared to a configuration in which heat exchange is constantly performed by the second heat exchange mode. As a result, it is possible to efficiently perform the heat exchange of the heat exchange target while suppressing an increase in power consumption.
  • the heat exchange target includes the heat exchange target fluid
  • the heat exchanger 1 further includes the second flow path 12 through which the heat exchange target fluid flows in a state of being in contact with the separate plate 10 on which the plurality of fin portions 13 a are provided.
  • the plurality of fin portions 13 a are disposed in parallel at the predetermined intervals p 1 in the width direction (Y direction) of the first flow path 11 through which air flows, and are formed to have the undulating shape from one end 11 b toward the other end 11 c of the first flow path 11 in the width direction of the first flow path 11 , and in performing the heat exchange of the heat exchange target, the first flow path 11 is configured to be used in both forced heat exchange where the heat exchange of the heat exchange target is performed by forcing air to flow into the first flow path 11 and natural heat exchange where the heat exchange of the heat exchange target is performed by natural convection.
  • the fin structure of the heat exchanger 1 capable of switching between performing heat exchange by natural convection and heat exchange by forcing air to flow in, and restraining the structure of the heat exchanger 1 from being complicated, like the above-described heat exchange system 100 .
  • the plurality of fin portions 13 a are disposed at the equal intervals over the whole width in the width direction (Y direction) of the first flow path 11 .
  • the plurality of fin portions 13 a are provided continuously from one end 11 b to the other end 11 c of the first flow path 11 , and undulate periodically such that the other end of the first flow path 11 is visible as viewed from one end 11 b of the first flow path 11 , a through flow path is formed in the first flow path 11 . Accordingly, it is possible to suppress an increase in pressure loss of air flowing in the first flow path 11 , compared to a configuration in which a through flow path is not formed in the first flow path 11 with the plurality of fin portions 13 a . As a result, even in a case where the plurality of fin portions 13 a have the undulating shape, it is possible to secure heat exchange efficiency in the second mode where heat exchange is performed by natural convection.
  • FIGS. 8 to 11 an angle range of a maximum inclination angle ⁇ (see FIG. 8 ) of a connecting portion 11 h (see FIG. 8 ) of each of a plurality of fin portions 131 (see FIG. 8 ) of a first corrugated fin 130 (see FIG. 8 ) according to a second embodiment will be described with reference to FIGS. 8 to 11 .
  • the same configurations as in the above-described first embodiment are represented by the same reference signs, and detailed description thereof will not be repeated.
  • the plurality of fin portions 131 according to the second embodiment have the same configuration as the plurality of fin portions 13 a according to the above-described first embodiment, except for a case where the maximum inclination angle ⁇ is different. As shown in FIG. 8 , the plurality of fin portions 131 undulate such that an undulating pattern having the same waveform is repeated at a fixed undulation width W in the width direction (Y direction) of the first flow path 11 .
  • the undulating pattern includes a crest portion 11 d that protrudes to one side (Y1 direction side) in the width direction of the first flow path 11 , a trough portion 11 e that protrudes to the other side (Y2 direction side), and a connecting portion 11 h that connects the crest portion 11 d and the trough portion 11 e .
  • the maximum inclination angle ⁇ of the connecting portion 11 h with respect to a direction (Z direction) from one end 11 b side toward the other end 11 c side of the first flow path 11 falls within an angle range of equal to or greater than 10 degrees and equal to or less than 30 degrees.
  • An example shown in FIG. 8 is a case where the maximum inclination angle ⁇ is 20 degrees.
  • each of the crest portion 11 d and the trough portion 11 e has a shape extending along a direction (Z direction) in which the first flow path 11 extends
  • the crest portion 11 d and the trough portion 11 e may not extend along the direction (Z direction) in which the first flow path 11 extends. That is, the connecting portions 11 h may be continuously connected to form an undulating pattern.
  • a contact that protrudes to one side (Y1 direction side) may be referred to as a crest portion
  • a contact that protrudes to the other side (Y2 direction side) may be referred to as a trough portion.
  • a period p 2 of undulation is determined by the disposition interval p 1 of the fin portions 131 and the maximum inclination angle ⁇ of the connecting portion 11 h .
  • the heat exchanger 1 is used in both the first mode and the second mode.
  • the period p 2 of undulation is set to a range based on a range of the disposition interval p 1 of the fin portions 131 , a range of the maximum inclination angle ⁇ of the connecting portion 11 h , and a heat discharge amount capable of using both the first mode and the second mode.
  • a lower limit value of the period p 2 of undulation is 0.5 times of the disposition interval p 1 of the fin portions 131 .
  • An upper limit value of the period p 2 of undulation is a value in a case where the first flow path 11 is configured such that the other end 11 c of the first flow path 11 is visible as viewed from one end 11 b of the first flow path 11 in a case where the disposition interval p 1 of the fin portions 131 is set to a range of equal to or greater than 5 mm and equal to or less than 10 mm, and the maximum inclination angle ⁇ of the connecting portion 11 h is set to be equal to or greater than 10 degrees and equal to or less than 30 degrees.
  • Simulation results of a heat exchange amount and a pressure loss in a case where the maximum inclination angle ⁇ of the connecting portion 11 h and the period p 2 of undulation are changed will be described with reference to FIGS. 9 to 11 .
  • Simulation results described below are results using a first corrugated fin 130 in which the maximum inclination angle ⁇ of the connecting portion 11 h in the heat exchanger 1 is set to 20 degrees, 10 degrees, and 30 degrees, the first corrugated fin 130 in which the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and a period p 3 of undulation is a half of the period p 2 of undulation, and a first corrugated fin 130 in which a period p 4 of undulation is two times of the period p 2 of undulation, as shown in FIG.
  • the simulation results described below also include a result using a first corrugated fin 140 in which the maximum inclination angle ⁇ of the connecting portion 11 h is 0 degrees (a so-called plain fin), as a comparative example.
  • a so-called plain fin As shown in FIG. 9 (F) , the first corrugated fin 140 according to the comparative example has a shape with no undulation in a fin portion.
  • connecting portion 11 h is disposed such that the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees.
  • the connecting portion 11 h is disposed such that the maximum inclination angle ⁇ of the connecting portion 11 h is 10 degrees.
  • the connecting portion 11 h is disposed such that the maximum inclination angle ⁇ of the connecting portion 11 h is 30 degrees.
  • the period of undulation of the first corrugated fin 130 a to the first corrugated fin 130 c is the period p 2 .
  • a first corrugated fin 130 d is configured such that the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 4 of undulation is a half of the period p 2 of undulation.
  • a first corrugated fin 130 e is configured such that the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 4 of undulation is two times of the period p 2 of undulation.
  • a graph G 3 shown in FIG. 10 takes a heat exchange amount as the vertical axis and takes a front face wind velocity as the horizontal axis.
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 10 degrees is shown by a one-dot chain line 30 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees is shown by a solid line 31 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 30 degrees is shown by a broken line 32 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 3 of undulation is a half of the period p 2 of undulation is shown by a two-dot chain line 33 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 4 of undulation is two times of the period p 2 of undulation is shown by a bold line 34 .
  • a simulation result according to the comparative example is shown by a bold dotted line 35 .
  • a case where the front face wind velocity is 0 (zero) means heat exchange by the second mode.
  • a case where the front face wind velocity is equal to or higher than 0 (zero) means heat exchange by the first mode.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 10 degrees shows that the heat exchange amount is increased with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 10 degrees shows that the heat exchange amount is about 1.4 times on average with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees shows that, in a case of the first mode, the heat exchange amount is about 1.7 times on average with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 30 degrees shows that, in a case of the first mode, the heat exchange amount is about 2.0 times on average with respect to the simulation result according to the comparative example.
  • both the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 3 of undulation is a half of the period p 2 of undulation and the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 3 of undulation is a half of the period p 2 of undulation show the substantially same heat exchange amount as the simulation result according to the comparative example.
  • the simulation result in a case where the period p 3 of undulation is a half of the period p 2 of undulation show that the heat exchange amount is increased with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 3 of undulation is a half of the period p 2 of undulation shows that, in a case of the first mode, the heat exchange amount is about 1.4 times on average compared to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 4 of undulation is two times of the period p 2 of undulation shows that the heat exchange amount is increased compared to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 4 of undulation is two times of the period p 2 of undulation shows that, in a case of the first mode, the heat exchange amount is about 1.7 times on average compared to the simulation result according to the comparative example.
  • the simulation result of the period p 4 of undulation shows the heat exchange amount equal to or greater than the simulation result of the period p 3 of undulation.
  • the heat exchange amount is large compared to the comparative example. It has been confirmed that, in a range of the maximum inclination angle ⁇ of the connecting portion 11 h of 10 degrees to 30 degrees, as the angle is increased, the heat exchange amount is increased. It has been confirmed that an influence of the period p 2 of undulation on the heat exchange amount is less than an influence of the maximum inclination angle ⁇ of the connecting portion 11 h on the heat exchange amount.
  • a graph G 4 shown in FIG. 11 takes a pressure loss as the vertical axis and takes a front face wind velocity as the horizontal axis.
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 10 degrees is shown by a one-dot chain line 36 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees is shown by a solid line 37 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 30 degrees is shown by a broken line 38 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 3 of undulation is a half of the period p 2 of undulation is shown by a two-dot chain line 39 .
  • a simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, and the period p 4 of undulation is two times of the period p 2 of undulation is shown by a bold line 40 .
  • a simulation result according to the comparative example is shown by a bold dotted line 41 .
  • a case where the front face wind velocity is 0 (zero) means heat exchange by the second mode.
  • a case where the front face wind velocity is equal to or higher than 0 (zero) means heat exchange by the first mode.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees shows that, in a case of the first mode, the pressure loss is about 2.8 times on average with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 30 degrees shows that, in a case of the first mode, the pressure loss is about 6.3 times on average with respect to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 3 of undulation is a half of the period p 2 of undulation shows that the pressure loss is increased compared to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 3 of undulation is a half of the period p 2 of undulation shows that, in a case of the first mode, the pressure loss is about 2.2 times compared to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 4 of undulation is two times of the period p 2 of undulation shows that the pressure loss is increased compared to the simulation result according to the comparative example.
  • the simulation result in a case where the period p 4 of undulation is two times of the period p 2 of undulation shows that, in a case of the first mode, the pressure loss is about 2.2 times on average compared to the simulation result according to the comparative example.
  • the pressure loss in a case of the first mode is the substantially same in the simulation result of the period p 4 of undulation and the simulation result of the period p 3 of undulation.
  • the maximum inclination angle ⁇ of the connecting portion 11 h falls within a range of equal to or greater than 10 degrees and equal to or less than 30 degrees. In a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, it has been confirmed that the angle can achieve both a heat discharge amount and heat exchange efficiency. Evaluation of the increasing rate of the heat exchange amount and evaluation of the efficiency of heat exchange are performed based on an amount of change in heat exchange amount and an amount of change in pressure loss with respect to a plane fin in a case where the maximum inclination angle ⁇ of the connecting portion 11 h is changed.
  • the efficiency of heat exchange is a value that is calculated by dividing the heat exchange amount by the pressure loss.
  • the plurality of fin portions 131 undulate such that the undulating pattern having the same waveform is repeated at the fixed undulation width W in the width direction (Y direction) of the first flow path 11 .
  • the undulating pattern includes the crest portion 11 d that protrudes to one side (Y1 direction side) in the width direction of the first flow path 11 , the trough portion 11 e that protrudes to the other side (Y2 direction side), and the connecting portion 11 h that connects the crest portion 11 d and the trough portion 11 e .
  • the maximum inclination angle ⁇ of the connecting portion 11 h with respect to the direction (Z direction) from one end 11 b side toward the other end 11 c side of the first flow path 11 falls within the angle range of equal to or greater than 10 degrees and equal to or less than 30 degrees.
  • the present inventors have conducted studies by a simulation and have confirmed that, in a case where the maximum inclination angle ⁇ of the connecting portion 11 h falls within the angle range of equal to or greater than 10 degrees and equal to or less than 30 degrees, it is possible to secure high performance in both heat exchange in the first mode and heat exchange in the second mode. In a case where the maximum inclination angle ⁇ of the connecting portion 11 h is 20 degrees, it has been confirmed that the angle can achieve both a heat discharge amount and heat exchange efficiency.
  • the first flow path 11 may be formed to extend in an oblique direction.
  • the heat exchanger 1 may be a fin and tube type heat exchanger other than a plate fin.
  • the invention may be applied to a heat sink.
  • a plurality of fin portions 61 a are provided to extend upward from a base portion 60 .
  • the base portion 60 is, for example, a metal member having a plate shape.
  • a space between a plurality of fin portions 61 a forms a first flow path 61 .
  • the heat sink 6 for example, a semiconductor element or the like is a heat exchange target, and the heat exchange of the semiconductor element or the like is performed by bringing the semiconductor element or the like into contact with the base portion 60 .
  • the plurality of fin portions 61 a are formed to have an undulating shape from one end 11 b toward the other end 11 c of the first flow path 11 in the width direction (Y direction) of the first flow path 11 of the plurality of fin portions 61 a . That is, the first flow path 11 may be divided by a plurality of fins in which an individual first fin portion is provided individually, not by a corrugated fin.
  • the first flow path 11 may be formed to extend in the up-down direction (Z direction), the first flow path 11 may be formed to extend in an oblique direction.
  • first and second embodiments although an example of a configuration in which the first flow path 11 and the second flow path 12 are perpendicular to each other has been shown, the invention is not limited thereto.
  • first flow path 11 and the second flow path 12 may be configured to face each other or the first flow path 11 and the second flow path 12 may be configured to be in parallel with each other.
  • first and second embodiments although an example of a configuration in which the first flow path 11 and the second flow path 12 are alternately laminated in the X direction has been shown, the invention is not limited thereto.
  • the first flow path 11 and the second flow path 12 may not be alternately laminated.
  • the first flow path 11 , the first flow path 11 , the second flow path 12 , the first flow path 11 , the first flow path 11 , the second flow path 12 , and the like may be laminated in this order.
  • the invention is not limited thereto.
  • the plurality of fin portions 13 a may not be disposed at equal intervals over the whole width in the Y direction.
  • the plurality of fin portions 13 a are not disposed at equal intervals over the whole width in the Y direction, since the structure of the heat exchanger 1 is complicated, it is preferable that the plurality of fin portions 13 a (the plurality of fin portions 131 ) are disposed at equal intervals over the whole width in the Y direction.
  • the invention is not limited thereto.
  • the undulation width W the plurality of fin portions 13 a may not be fixed.
  • the undulation width W of the plurality of fin portions 13 a (the plurality of fin portions 131 ) is fixed, since the structure of the heat exchanger 1 is complicated, it is preferable that the undulation width W of the plurality of fin portions 13 a (the plurality of fin portions 131 ) is fixed.
  • the invention is not limited thereto.
  • the plurality of fin portions 13 a may have an undulating shape in which undulating patterns having different waveforms are combined.
  • the plurality of fin portions 13 a (the plurality of fin portions 131 ) have an undulating shape in which undulating patterns having different waveforms are combined, since the structure of the heat exchanger 1 is complicated, it is preferable that the plurality of fin portions 13 a (the plurality of fin portions 131 ) undulate such that the pattern having the same waveform is repeated.
  • the interval p 1 of the plurality of fin portions 13 a (the plurality of fin portions 131 ) is about 8 mm
  • the interval p 1 of the plurality of fin portions 13 a may be, for example, about 6 mm or may be about 9 mm.
  • the interval p 1 of the plurality of fin portions 13 a is within a range of equal to or greater than 5 mm and equal to or less than 10 mm, the interval p 1 of the plurality of fin portions 13 a (the plurality of fin portions 131 ) may have any value.
  • the invention is not limited thereto.
  • the crest portion 11 d and the trough portion 11 e may be connected by a connecting portion in which the angle changes continuously.
  • the first flow path 11 may be a so-called sine curve shape in top view. In a case where the first flow path 11 has a sine curve shape, a maximum angle of the connecting portion in which the angle continuously changes may fall within an angle range of equal to or greater than 10 degrees and equal to or less than 30 degrees.
  • control unit 3 switches between the first mode and the second mode based on the temperature difference between air and the heat exchange target
  • the invention is not limited thereto.
  • an input reception unit that receives an input of a user may be provided, and the control unit 3 may be configured to switch between the first mode and the second mode based on an input signal of the user.
  • the fan 2 may be provided in the opening 11 a on the Z1 direction side. That is, in the first mode, heat exchange may be performed by forcing air to flow in from the Z1 direction side with the fan 2 , and in the second mode, heat exchange may be performed by making air flow in from the Z2 direction side by natural convection.
  • the position where the fan 2 is provided may be any of the opening 11 a on the Z1 direction side and the opening 11 a on the Z2 direction side.
  • the fan 2 may be configured to make air flow into the first flow path 11 by sucking air.
  • the fan 2 may not be configured to cover the opening 11 a .
  • the fan 2 may be connected by a duct, a casing, or the like and may be provided at a remote position.
  • the heat exchanger 1 may b configured to perform heating of the heat exchange target.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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PCT/JP2021/013615 WO2021200992A1 (ja) 2020-03-31 2021-03-30 熱交換システムおよび熱交換器のフィン構造

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ES3010457T3 (en) * 2022-09-20 2025-04-03 Alfa Laval Vicarb Heat exchanger module
PL446756A1 (pl) 2023-11-17 2025-05-19 Aic Spółka Akcyjna Konstrukcja powierzchni wymiany ciepła, płyta wymiennika ciepła i sposób jej wytwarzania, oraz wymiennik ciepła
JP7727226B1 (ja) * 2024-03-18 2025-08-21 ダイキン工業株式会社 熱交換器及び冷凍装置

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JP7408779B2 (ja) 2024-01-05
EP4130627C0 (en) 2025-09-03
EP4130627A4 (en) 2023-09-13
WO2021200992A1 (ja) 2021-10-07
JPWO2021200992A1 (https=) 2021-10-07
US20230160637A1 (en) 2023-05-25
EP4130627A1 (en) 2023-02-08
EP4130627B1 (en) 2025-09-03

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